Electric control apparatus for shock absorber

Abstract

 An electric control apparatus for a shock absorber disposed between unsprung mass and sprung mass of a suspension mechanism in an automative vehicle and provided with an electrically operated control valve (14a) for changing damping characteristics of vertical displacement of the sprung mass relative to the unsprung mass, wherein absolute vertical displacement velocity (V_Z1) of the sprung mass and relative vertical displacement velocity (V_Y1) of the sprung mass to the unsprung mass are detected to determine a target opening degree (X_S1) of the control valve (14a) in accordance with the detected absolute vertical displacement velocity (V_Z1) and relative vertical displacement velocity (V_Y1) of the sprung mass, and where variation of the target opening degree (X_S1) is allowed in a large range only when the direction of the relative vertical displacement velocity (V_Y1) has changed and is restricted in a predetermined small range under other conditions where the shock absorber acts to absorb vibration of the vehicle body.

Description

[0001] The present invention relates to an electric control apparatus for a shock absorber disposed between unsprung mass and sprung mass of a suspension mechanism in an automotive vehicle and provided with an electrically operated control valve to be electrically controlled for changing damping characteristics of vertical displacement of the sprung mass relative to the unsprung mass.

[0002] Disclosed in Japanese Patent Laid-open Publication No. 3-276807 is a conventional electric control apparatus of this kind, wherein absolute vertical displacement velocity of the sprung mass and relative vertical displacement velocity of the sprung mass to the unsprung mass are detected to control the damping coefficient of the shock absorber on a basis of the skyhook theory proposed by D. Karnopp. In this control apparatus, an opening degree of the control valve is decreased in accordance with an increase of a difference between the absolute vertical displacement velocity and the relative vertical displacement velocity to increase the damping coefficient of the shock absorber and is increased in accordance with a decrease of the difference between the absolute vertical displacement velocity and the relative vertical displacement velocity to decrease the damping coefficient of the shock absorber.

[0003] In such control of the damping coefficient, however, the difference between the absolute vertical displacement velocity and the relative vertical displacement velocity changes from a positive value to a negative value or vice-versa if either the absolute vertical displacement velocity or the relative vertical displacement velocity changes in its sign from positive to negative or vice-versa. In such an instance, the opening degree of the control valve is greatly changed to cause sudden change of the damping coefficient of the shock absorber. In other words, when the relative vertical displacement velocity is maintained to be approximately zero, the damping force of the shock absorber is changed in a small range, In this instance, the passenger is not applied with any large shock. If the relative vertical displacement velocity is not maintained to be approximately zero, the damping force of the shock absorber changes in a large range. In this instance, the passenger is applied with a large shock.

[0004] It is, therefore, a primary object of the present invention to provide an electric control apparatus for a shock absorber capable of controlling the control valve in such a manner that the passenger is not applied with any large shock even when the damping characteristic of the shock absorber is switched over.

[0005] According to the present invention, the object is accomplished by providing an electric control apparatus for a shock absorber disposed between unsprung mass and sprung mass of a suspension mechanism in an automotive vehicle and provided with an electrically operated control valve to be electrically controlled for changing damping characteristics of vertical displacement of the sprung mass relative to the unsprung mass, which control apparatus comprises first detection means for detecting absolute vertical displacement velocity of the sprung mass; second detection means for detecting relative vertical displacement velocity of the sprung mass to the unsprung mass; determination means for determining a target opening degree of the control valve in accordance with the detected absolute vertical displacement velocity and relative vertical displacement velocity of the sprung mass; restriction means for allowing variation of the target opening degree in a large range only when the direction of the relative vertical displacement velocity has changed and for restricting the target opening degree in a predetermined small range under other conditions where the shock absorber acts to absorb vibration of the vehicle body; and control means for controlling an opening degree of the control valve to the target opening degree.

[0006] For a better understanding of the present invention, and to show how the same may be carried into effect, reference will now be made, by way of example, to the accompanying drawings, in which:

Fig. 1 is a schematic block diagram of an electric control apparatus for shock absorbers in accordance with the present invention;

Figs. 2(A) to 2(D) each illustrate a conversion characteristic of each conversion table shown in Fig. 1;

Fig. 3 is a graph showing a conversion characteristic of a conversion table in a valve opening degree table circuit shown in Fig. 1;

Fig. 4 is a flow chart of a control program executed by a microcomputer of a restriction circuit shown in Fig. 1; and

Figs. 5(a) to 5(d) each are a time chart respectively showing variation of absolute vertical displacement velocity of sprung mass, relative vertical displacement velocity of the sprung mass to unsprung mass, a target opening degree and an instant target opening degree.

[0007] In Fig. 1 of the drawings, there is schematically illustrated an electric control apparatus for shock absorbers 10A-10D which are disposed between unsprung mass in the form of a lower arm of a suspension mechanism (not shown) and sprung mass in the form of a vehicle body structure (not shown) at each position of left and right front road wheels and left and right rear road wheels. The shock absorbers 10A-10D include hydraulic cylinders 12a-12d each interior of which is subdivided into upper and lower chambers by means of pistons 11a-11d. The hydraulic cylinders 12a-12d are mounted on the unsprung mass, and the pistons 11a-11d are connected to each lower end of piston rods 13a-13d which are supported on the sprung mass at their upper ends. The upper and lower chambers of hydraulic cylinders 12a-12d are communicated with each other respectively through electromagnetic control valves 14a-14d whose each opening degree can be adjusted at plural steps. The lower chambers of hydraulic cylinders 12a-12d are respectively connected to gas spring units 15a-15d which are constructed to absorb volume change of the lower and upper chambers caused by vertical displacements of the piston rods 13a-13d.

[0008] The electric control apparatus includes relative displacement sensors 21a-21d respectively disposed between the sprung mass and unsprung mass at each road wheel to detect relative vertical displacement amounts L_Y1, L_Y2, L_Y3, L_Y4 of the sprung mass to the unsprung mass. Electric signals respectively indicative of the detected relative vertical displacement amounts L_Y1, L_Y2, L_Y3, L_Y4 are differentiated by differentiators 22a-22d and issued as electric signals indicative of relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4 of the sprung mass to the unsprung mass. Increase of the relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4 is represented by a positive value, while decrease of the relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4 is represented by a negative value.

[0009] The electric control apparatus further includes vertical acceleration sensors 23a-23d mounted on the sprung mass at each road wheel to detect absolute vertical acceleration A_Z1, A_Z2, A_Z3, A_Z4 of the sprung mass. Electric signals indicative of the detected vertical acceleration A_Z1, A_Z2, A_Z3, A_Z4 are integrated by integrators 24a-24d and issued as electric signals indicative of the absolute vertical displacement velocity V_Z1, V_Z2, V_Z3, V_Z4 of the sprung mass. The absolute vertical displacement velocity V_Z1, V_Z2, V_Z3, V_Z4 of the sprung mass in an upward direction is represented by a positive value, while the absolute vertical displacement velocity V_Z1, V_Z2, V_Z3, V_Z4 of the sprung mass in a downward direction is represented by a negative value.

[0010] A movement mode analyzing circuit 25 is connected to the integrators 24a-24d to analyze the absolute vertical displacement velocity V_Z1, V_Z2, V_Z3, V_Z4 into roll velocity V_ZR of the vehicle body, pitch velocity V_ZP, heave velocity V_ZH (vertical displacement velocity of the vehicle body) and warp velocity V_ZW (torsion velocity of the vehicle body in a fore-and-aft direction). In a practical embodiment, the analysis of the movement mode is realized by calculation of the following coordinate conversion formula.


   Each output of the movement mode analyzing circuit 25 is connected to each first input of multiplexers 26a-26d which are connected at their second inputs to a steering angle sensor 27a, a vehicle speed sensor 27b, a brake sensor 27c, an accelerator sensor 27d, a differentiator 27e, conversion tables 28a-28d and a damping coefficient generator 29. The steering sensor 27a is mounted on a steering shaft of the vehicle (not shown) to detect a rotation angle of a steering wheel for producing an electric signal indicative of a steering angle ϑf corresponding with the detected rotation angle. The vehicle speed sensor 27b is arranged to detect rotation speed of an output shaft of a transmission of the vehicle as a vehicle speed SP for producing an electric signal indicative of the detected vehicle speed SP. The brake sensor 27c is arranged to detect a depression amount BR of a brake pedal (not shown) for producing an electric signal indicative of the detected depression amount BR. The accelerator sensor 27d is arranged to detect a depression amount AC of an accelerator pedal (not shown) for producing an electric signal indicative of the detected depression amount AC. The differentiator 27e is connected to the steering sensor 27a to differentiate the electric signal indicative of the steering angle ϑf for producing an electric signal indicative of a steering speed dϑf/dt.

[0011] The conversion tables 28a-28d are applied with the electric signals respectively indicative of the steering speed dϑf/dt, vehicle speed SP, depression amount BR of the brake pedal and depression amount AC of the accelerator pedal and convert the applied electric signals into electric signals respectively indicative of exponents P_ST, P_SP, P_BR, P_AC which are changed as shown in Figs. 2(A)-2(D). The damping coefficient generator 29 is applied with the electric signals indicative of the exponents P_ST, P_SP, P_BR, P_AC and calculates the following equations to obtain Skyhook damping coefficients C_R, C_P, C_H, C_W as target damping coefficients respectively corresponding with roll motion, pitch motion, heave motion and warp motion of the vehicle body.














   The multiplexers 26a-26d are responsive to the electric signals from the movement mode analysis circuit 25 and damping coefficient generator 29 to multiply the target skyhook damping coefficients C_R, C_P, C_H, C_W by the movement velocity V_ZR, V_ZP, V_ZH, V_ZW at each motion of the vehicle roll, pitch, heave and warp. Thus, the multiplexers 26a-26d produce electric signals indicative of target damping forces C_R·V_ZR, C_P·V_ZP, C_H·V_ZH, C_W·V_ZW and apply them to a movement mode composition circuit 31. The movement mode composition circuit 31 is responsive to the electric signals from the multiplexers 26a-26d to composite the target damping forces C_R·V_ZR, C_P·V_ZP, C_H·V_ZH, C_W·V_ZW with the corresponding vertical damping forces C₁₀·V_Z10, C₂₀·V_Z20, C₃₀·V_Z30, C₄₀·V_Z40 of the sprung mass. Practically, the composition of the movement mode is realized by calculation of the following coordinate conversion formula.


In the formula (3), the coefficients C₁₀, C₂₀, C₃₀, C₄₀ correspond with skyhook damping coefficients against vertical movement of the sprung mass at each road wheel, and the characters V_Z10, V_Z20, V_Z30, V_Z40 correspond with the absolute vertical displacement velocity V_Z1, V_Z2, V_Z3, V_Z4 of the sprung mass.

[0012] The movement mode analyzing circuit 25 and the movement mode composition circuit 31 have been adapted for the following reason. The shock absorbers 10A-10D act to control a damping force against vertical movement of the sprung mass relative to the unsprung mass at each road wheel, while the passenger feels each motion of the vehicle roll, pitch, heave and warp. It is, therefore, desirable that the vertical movement of the vehicle body is controlled in consideration with the skyhook damping coefficients C_R, C_P, C_H, C_W which are defined in accordance with driving conditions of the vehicle such as the steering speed dϑf/dt, vehicle speed SP, depression amount BR of the brake pedal and depression amount AC of the accelerator pedal.

[0013] The electric control apparatus further includes a valve opening degree table circuit 32 and a comparator 33 which are provided to correspond with the respective shock absorbers 10A-10D. In the figure, there are illustrated only the valve opening degree table circuit 32 and comparator 33 for the shock absorber 10A. The valve opening degree table circuit 32 and comparator 33 are applied with the electric signals indicative of the relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4 from the differentiators 22a-22d and the electric signals indicative of the vertical damping forces C₁₀ V_Z10, C₂₀ V_Z20, C₃₀ V_Z30, C₄₀ V_Z40 of the sprung mass from the movement mode composition circuit 31. In this instance, the electric signals indicative of the vertical damping forces C₁₀·V_Z10, C₂₀·V_Z20, C₃₀·V_Z30, C₄₀·V_Z40 of the sprung mass represent each value of the absolute vertical displacement velocity V_Z1, V_Z2, V_Z3, V_Z4 compensated by the coefficients C₁₀, C₂₀, C₃₀, C₄₀. The valve opening degree table circuit 32 includes a calculator and a characteristic table shown in Fig. 3, which is designed to produce an electric signal indicative of a valve opening degree X_SIX corresponding with the relative vertical displacement velocity V_Y1 and damping coefficient C₁₀ V_Z10. The valve opening degree X_SIX is increased in accordance with a decrease of the relative vertical displacement velocity V_Y1 and is also increased in accordance with an increase of the absolute vertical displacement velocity V_Z10 or an increase of the coefficients C₁₀, C₂₀, C₃₀, C₄₀.

[0014] A select circuit 34 is connected to the valve opening degree table circuit 32 to be applied with the electric signal indicative of the valve opening degree therefrom and is connected to a maximum valve opening degree generator 35 to be applied with an electric signal indicative of a maximum opening degree X_S10 therefrom. The comparator 33 is arranged to compare the relative vertical displacement velocity V_Y1 with the damping force C₁₀·V_Z10 for issuing a high level signal therefrom when the sign of the relative vertical displacement velocity V_Y1 coincides with the sign of the damping force C₁₀ and for issuing a low level signal therefrom when the sign of the relative vertica ment velocity V_Y1 does not coincide with the sign of the damping force C₁₀·V_Z10. Thus, the select circuit 34 act to issue the electric signal indicative of the valve opening degree X_SIX as an electric signal indicative of a target opening degree X_S1 in response to the high level signal from the comparator 33 and to issue an electric signal indicative of the maximum valve opening degree X_S10 as the electric signal indicative of the target opening degree X_S1 in response to the low level signal from the comparator 33.

[0015] In this embodiment, means for determining the target opening degree X_S1 of the electromagnetic control valve 14a is composed of the valve opening degree table circuit 32, comparator 33, select circuit 34 and maximum opening degree generator 35. The target opening degree X_S1 is determined in such a manner as described above for the following reason. In a condition where the shock absorber 10A is being shrunk due to a projection on the travel road during upward displacement of the sprung mass, the damping force C₁₀ V_Z10 becomes positive while the relative vertical displacement velocity V_Y1 becomes negative. In a condition where the shock absorber 10A is extended due to a hollow spot on the travel road during downward movement of the unsprung mass, the damping force C₁₀·V_Z10 becomes negative while the relative vertical displacement velocity V_Y1 becomes positive. Under these conditions, the shock absorber 10A does not act to absorb vibration of the vehicle body. Thus, the opening degree of the electromagnetic control valve 14a is maximized under the above conditions to render the shock absorber 10A in a soft condition and is controlled in accordance with the relative vertical displacement velocity V_Y1 and damping force C₁₀·V_Z10 under other conditions where the shock absorber 10A acts to absorb vibration of the vehicle body.

[0016] The electric signal indicative of the target opening degree X_S1 is applied to a restriction circuit 36 which includes a microcomputer arranged to be applied with the electric signal indicative of the relative vertical displacement velocity V_Y1 from the differentiator 22a. The microcomputer of restriction circuit 36 is programmed to repeat execution of a control program shown by a flow chart in Fig. 4 for allowing variation of the target opening degree X_S1 in a larger range only when the direction of the relative vertical displacement velocity V_Y1 has changed and for restricting variation of the target opening degree X_S1 in a predetermined small range under other conditions where the shock absorbers 10A-10d act to absorb vibratin of the vehicle body. The restriction circuit 36 is connected to a driving circuit 37 which is provided to drivingly control the electromagnetic control valve 14a in accordance with an electric signal indicative of a target opening degree X_S1(n) restricted at the restriction circuit 36 for setting the opening degree of control valve 14a to the restricted target opening degree X_S1(n).

[0017] In operation of the electric control apparatus, relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4 of the sprung mass to the unsprung mass at each road wheel is detected by the relative displacement sensor 21a-21d and differentiators 22a-22d to apply electric signals indicative of the relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4 to the valve opening degree table circuit 32, comparator 33 and restriction circuit 36. On the other hand, absolute vertical displacement velocity V_Z1, V_Z2, V_Z3, V_Z4 of the sprung mass at each road wheel is detected by the acceleration sensor 23a-23d and integrators 24a-24d and analyzed by the movement mode analyzing circuit 25 into roll velocity V_ZR, pitch velocity V_ZP, heave velocity V_ZH and warp velocity V_ZW of the sprung mass. Thus, electric signals indicative of the analyzed velocity V_ZR, V_ZP, V_ZH, V_ZW are applied to the multiplexers 26a-26d. Simultaneously, a steering speed dϑf/dt, a vehicle speed SP, a depression amount BR of the brake pedal and a depression amount AC of the accelerator pedal are detected by the sensors 27a, 27b, 27c, 27d and differentiator 27e and converted by the conversion tables 28a-28d into electric signals indicative of exponents P_ST, P_SP, P_BR, P_AC shown in Figs. 2(A)-2(D). When applied with the electric signals indicative of the exponents P_ST, P_SP, P_BR, P_AC, the damping coefficient generator 29 calculates the equations (2) to obtain skyhook damping coefficients C_R, C_P, C_H, C_W for optimal control of roll motion, pitch motion, heave motion and warp motion of the vehicle body and applies electric signals indicative of the skyhook damping coefficients C_R, C_P, C_H, C_W to multipliers 26a-26d. At the multipliers 26a-26d, the skyhook damping coefficients C_R, C_P, C_H, C_W are respectively multiplied by the roll velocity V_ZR, pitch velocity V_ZP, heave velocity V_ZH and warp velocity V_ZW to obtain target damping forces C_R·V_ZR, C_P·V_ZP, C_H·V_ZH, C_W·V_ZW with respect to the roll motion, pitch motion, heave motion and warp motion of the vehicle body. Thus, the target damping forces C_R·V_ZR, C_P·V_ZP, C_H·V_ZH, C_W·V_ZW are converted by the movement mode composition circuit 31 into target damping forces C₁₀·V_Z10, C₂₀·V_Z20, C₃₀·V_Z30, C₄₀·V_Z40 with respect to the absolute vertical movement of the sprung mass at each road wheel to apply electric signals indicative of the target damping forces C₁₀·V_Z10, C₂₀·V_Z20, C₃₀·V_Z30, C₄₀· V_Z40 to the valve opening degree table circuit 32 and comparators 33.

[0018] When each sign of the target damping forces C₁₀ V_Z10, C₂₀·V_Z20, C₃₀·V_Z30, C₄₀·V_Z40 coincides with each sign of the relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4, a target opening degree X_SIX of the control valve is determined in accordance with the relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4 and the target damping forces C₁₀·V_Z10, C₂₀·V_Z20, C₃₀·V_Z30, C₄₀·V_Z40 at the valve opening degree table circuit 32, comparator 33, select circuit 34 and maximum valve opening degree generator 35. (see Fig. 3) When each sign of the target damping forces C₁₀·V_Z10, C₂₀·V_Z20, C₃₀·V_Z30, C₄₀·V_Z40 does not coincide with each sign of the relative vertical displacement velocity V_Y1, V_Y2, V_Y3, V_Y4, the maximum opening degree X_S10 is determined as the target opening degree X_S1X of control valve 14a. Assuming that the absolute vertical displacement velocity V_Z1 of the sprung mass and the relative vertical displacement velocity V_Y1 of the sprung mass to the unsprung mass has changed as shown in Figs. 5(a) and 5(b), the target opening degree X_S1 of damper valve 14a is changed as shown in Fig. 5(c). Thus, electric signals respectively indicative of the target opening degree X_S1 and the relative vertical displacement velocity V_Y1 are applied to the restriction circuit 36.

[0019] At the restriction circuit 36, the microcomputer repeats execution of the control program shown by the flow chart in Fig. 4. After initiated execution of the control program at step 100, the computer is applied with electric signals indicative of the relative vertical displacement velocity V_Y1 and target opening degree X_S1 at step 102 and 104 and sets the relative vertical displacement velocity V_Y1 and target opening degree X_S1 as instant relative vertical displacement velocity V_Y1(n) and instant target opening degree X_S1(n). At the following step 106, the computer compares the sign [V_Y1(n)] of the instant relative vertical displacement velocity V_Y1(n) with the sign [V_Y1(n-1)] of a previous relative vertical displacement velocity V_Y1(n-1) previously set at step 118. If the relative vertical displacement velocity V_Y1(n) is maintained in a positive value until a time t₃ as shown in Fig. 5(b), the computer determines a "Yes" answer at step 106 and causes the program to proceed to step 108-114.

[0020] During processing at step 108-114, variation of the target opening degree X_S1 is restricted within a predetermined small value ΔX (for instance, a value corresponding with one step of the opening degree of control valve 14a) as described below. If an absolute value

of a difference between the instant target opening degree X_S1(n) and the previous target opening degree X_S1(n - 1) is less than the predetermined small value ΔX, the computer determines a "Yes" answer at step 108 and produces at step 116 an electric signal indicative of the instant target opening degree X_S1(n). If the absolute value

is more than the predetermined small value ΔX, the computer determines a "No" answer at step 108 and changes the instant target opening degree X_S1(n) by processing at step 110-114 as follows. If the instant target opening degree X_S1(n) tends to be decreased, the computer determines a "Yes" answer at step 110 and causes the program to proceed to step 112 where the instant target opening degree X_S1(n) is changed to a small value

less than the previous target opening degree X_S1(n - 1). If the target opening degree X_S1(n) tends to be increased, the computer determines a "No" answer at step 110 and causes the program to proceed to step 114 where the instant target opening degree X_S1(n) is changed to a larger value

than the previous target opening degree X_S1(n - 1).

[0021] Thus, when the target opening degree X_S1 changes in a small range until a time t₁ shown in Fig. 5(c), the instant target opening degree X_S1(n) is determined to be equal to the target opening degree X_S1. When the target opening degree X_S1 changes in a large range at the time t₁ shown in Fig. 5(c), the instant target opening degree X_S1(n) is changed by the predetermined value ΔX at plural steps. Assuming that the relative vertical displacement velocity V_Y1 changes from positive to negative at the time t₃ shown in Fig. 5(b), the computer determines a "No" answer at step 106 and causes the program to proceed to step 116. In this instance, the instant target opening degree X_S1(n) greatly changes in accordance with an increase of the target opening degree X_S1. At step 116, the computer produces an electric signal indicative of the instant target opening degree X_S1(n) and applies it to the driving circuit 37. When applied with the electric signal, the driving circuit 37 sets the opening degree of control valve 14a to the instant target opening degree X_S1(n). As a result, the damping force of shock absorber 10A is controlled at plural steps in accordance with the instant target opening degree X_S1(n). After processing at step 116, the computer renews at step 118 the previous relative vertical displacement velocity V_Y1(n - 1) and the previous target opening degree X_S1(n - 1) with the instant relative vertical displacement velocity V_Y1(n) and target opening degree X_S1(n) for the following execution of the control program.

[0022] As is understood from the above description, great change of the damping force of the shock absorbers 10A-10D is permitted only when the direction of relative vertical displacement velocity V_Y1-V_Y4 of the sprung mass to the unsprung mass has changed. Under the other conditions, variation of the damping force of the shock absorbers 10A-10D is restricted within the predetermine small value ΔX. Thus, shocks of the passenger can be restrained in a minimum value without causing any loss of damping effects by the shock absorbers 10A-10D based on the skyhook theory.

[0023] Although in the above embodiment, the differentiators 22a-22d, 27e, integrators 24a-24d, movement mode analyzing circuit 25, multiplexers 26a-26d, damping coefficient generator 29, movement mode composition circuit 31, valve opening degree table circuit 32, comparator 33, select circuit 34 and maximum valve opening degree generator 35 have been constructed in the form of a hard circuit, either or all the circuits may be replaced with a control program processed by a microcomputer. Alternatively, the processing of the control program may be carried out by means of a hard circuit.

[0024] An electric control apparatus for a shock absorber disposed between unsprung mass and sprung mass of a suspension mechanism in an automative vehicle and provided with an electrically operated control valve (14a) for changing damping characteristics of vertical displacement of the sprung mass relative to the unsprung mass, wherein absolute vertical displacement velocity (V_Z1) of the sprung mass and relative vertical displacement velocity (V_Y1) of the sprung mass to the unsprung mass are detected to determine a target opening degree (X_S1) of the control valve (14a) in accordance with the detected absolute vertical displacement velocity (V_Z1) and relative vertical displacement velocity (V_Y1) of the sprung mass, and where variation of the target opening degree (X_S1) is allowed in a large range only when the direction of the relative vertical displacement velocity (V_Y1) has changed and is restricted in a predetermined small range under other conditions where the shock absorber acts to absorb vibration of the vehicle body.

Claims

1. An electric control apparatus for a shock absorber disposed between unsprung mass and sprung mass of a suspension mechanism in an automotive vehicle and provided with an electrically operated control valve (14a) to be electrically controlled for changing damping characteristics of vertical displacement of the sprung mass relative to the unsprung mass, comprising:
   first detection means (23a, 24a) for detecting absolute vertical displacement velocity (V_Z1) of the sprung mass;
   second detection means (21a, 22a) for detecting relative vertical displacement velocity (V_Y1)of the sprung mass to the unsprung mass;
   determination means (32) for determining a target opening degree (X_S1) of the control valve (14a) in accordance with the detected absolute vertical displacement velocity (V_Z1) and relative vertical displacement velocity (V_Y1) of the sprung mass;
   restriction means (36) for allowing variation of the target opening degree in a large range only when the direction of the relative vertical displacement velocity (V_Y1) has changed and for restricting the target opening degree (X_S1) in a predetermined small range under other conditions where the shock absorber acts to absorb vibration of the vehicle body; and
   control means for controlling an opening degree of the control valve (14a) to the target opening degree (X_S1).

2. An electric control apparatus for a shock absorber as claimed in Claim 1, further comprising means (29) for generating an electric signal indicative of a target damping coefficient (C_R) against vertical movement of the sprung mass in accordance with driving conditions of the vehicle and means (25, 26a, 31) for determining a target damping force (C₁₀·V_Z10) in accordance with the absolute vertical displacement velocity (V_Z1) and the target damping coefficient (C_R), wherein said determination means (32) is arranged to determine a target opening degree (X_S1) of said control valve in accordance with the relative vertical displacment velocity (V_Y1) of the sprung mass and the target damping force (C₁₀·V_Z10).

3. An electric control apparatus for a shock absorber as claimed in Claim 2, further comprising means (35) for generating an electric signal indicative of a maximum valve opening degree (X_S10) therefrom, comparison means (33) arranged to compare the relative vertical displacement velocity (V_Y1) with the target damping force (C₁₀·V_Z10) for issuing a first signal when a sign of the relative vertical displacement velocity coincides with a sign of the target damping force and for issuing a second signal when the sign of the relative vertical displacement velocity does not coincide with the sign of the target damping force, and selection means (34) for applying an electric signal indicative of the target opening degree (X_S1) to said restiction means (36) in response to the first signal from said comparison means and for applying an electric signal indicative of the maximum valve opening degree (X_S10) to said restriction means in response to the second signal from said comparison means.

4. An electric control system for a shock absorber disposed between unsprung mass and sprung mass of a suspension mechanism in an automotive vehicle and provided with an electrically operated control valve (14a) the opening degree of which is electrically controlled for changing damping characteristics of vertical displacement of the sprung mass relative to the unsprung mass, wherein absolute vertical displacement velocity (V_Z1) of the sprung mass and relative vertical displacement velocity (V_Y1) of the sprung mass to the unsprung mass are detected to determine a target opening degree (X_S1) of the control valve (14a) in accordance with the detected absolut vertical displacement velocity (V_Z1) and relative vertical displacement velocity (V_Y1) of the sprung mass, and
   wherein the control system comprises restriction means (36) for allowing free variation of the target opening degree (X_S1) only in a condition where the shock absorber does not act to absorb vibration of the vehicle body and for restricting variation of the target opening degree (X_S1) in a predetermined range in a condition where the shock absorber acts to absorb vibration of the vehicle body.

Drawing